High energy impact machines



Aug. 22, 1967 J. B. OTTESTAD ETAL 3,336,788

HIGH ENERGY IMPACT MACHINES 6 Sheets-Sheet 1 Filed April 1, 1964 w T N E/V m w W 5 m u r/Q fi u F JACK B. OTTESTAD QERALD J. FARRELL Aug. 22,1967 J. B. OTTESTAD ETAL 3, 36,788

HIGH ENERGY IMPACT MACHINES Filed April 1, 1964 6 Sheets-$heet 2 f TZ YCwl w "i Wu, q]

AI-IgQZZ, 1967 J. B. OTTESTAD ETAL 3,336,788

I HIGH ENERGY IMPACT MACHINES Filed April 1, 1964 6 Sheets-Sheet 5INVENTORS JACK B. OTTESTAD GERALD .J. FARRELL Aug. 22, 1957 J. B.OTTESTAD ETAL 3,336,788

' HIGH ENERGY I MPACT MACHINES Filed April 1, 1964 e Sheets-Sheet 4 mumgu III JIHEHHI JACK B. OTTESTAD GERALD B. FARRELL li w MvQA United StatesPatent 3,336,788 HIGH ENERGY IMPACT MACHINES Jack B. Ottestad, La Jolla,Calif., and Gerald J. Farrell, Park Forest, 111., assignors to US.Industries, Inc., New York, N.Y., a corporation of Delaware Filed Apr.1, 1964, Ser. No. 356,544 15 Claims. (Cl. 72-453) ABSTRACT OF THEDISCLOSURE High energy impact machine wherein driver piston is isolatedfrom the source of working fluid used in driving it, when the machine iscocked and ready to fire, and firing is triggered by the feeding ofworking fluid from said source to the portion of said piston acted uponby said working fluid during driving thereof.

machines have proven to be highly practical and successful in operation.It is an important object of the present invention to affordimprovements over such high-energy rate mchines as have been heretoforeknown in the art.

In high-energy impact machines of the type to which the presentinvention relates, two plates are moved together by a suitablepressurized elastic medium such as a compressed gas, forcing a driverpiston and a cylinder to move in opposite directions. In such machinesthe pressure exerted on the pistons and cylinders is relatively high,such as, for example, 1,500 pounds per square inch, or more, with theplates delivering 145,000 foot pounds of energy, or more, at impact.Also, in such machines it is not uncommon for the plates thereof toaccelerate from a stationary condition to a closure rate of 50 feet persecond, or more, in a total stroke distance between the two plates oftwelve inches.

High-energy impact machines of the preferred type of construction shownherein, and in the aforementioned copending application, Ser. No.190,524, now Patent No. 3,135,140, embody two driver assemblies, eachincluding a driver piston and a cylinder. In the operation thereof, whenthe machine is cocked and ready to be fired, the pistons are disposed insuch position in the respective cylinders that they are effective toprevent the flow of the high pressure gas, by which the driverassemblies are to be actuated, from the source thereof into thecylinders; and, thereafter, in firing the machines, the pistons aremoved out of such cocked position into a firing position effective topermit the gas to flow into position in the cylinders effective to drivethe pistons and cylinders apart, the flow of gas into the cylindersbeing so rapid, when the pistons are moved into the firing positino,that the driver assemblies are substantially instantaneously subjectedto the full pressure of the source of gas. Under such conditions, theacceleration of the driver assemblies is very fast. Therefore, if in themovement of the pistons from cocked position to firing position, onepiston leads the other into firing position by even a minute fraction ofa second, the tendency to tilt the platesice plates places an excessivestrain on the machine, tending to force the guides for the platesoutwardly away from each other, among other things. It is an importantobject of the present invention to insure that the driver pistons ofsuch high-energy impact machines all move simultaneously into firingposition without any time lag between them.

An object ancillary to the foregoing is to effect the movement of allsuch pistons in such a machine into firing position in a novelexpeditious manner.

Another object of the present invention is to afford a novel machine ofthe aforementioned type wherein such movement of all of the pistonsthereof into firing position may be simultaneously effected in a noveland expeditious manner by gas pressure.

Another object is to afford a novel machine of the aforementioned typewherein the pressurized gas from the source used to fire the machine maybe used to move the pistons into such firing positions.

A further object is to afford a novel machine of the aforementioned typeembodying a novel chamber, constituted and arranged in a novel andexpeditious manner therein for storing the pressurized gas used infiring the machine.

In high-energy impact machines heretofore known in the art of the typeto which the present invention appertains, the driver pistons thereofhave commonly embodied bleed passageways therethrough, the bleedpassageways opening at both ends thereof into a respective end portionof the cylinders in which the pistons are disposed. With suchconstruction, when the high pressure gas flows into the cylinders on oneside of the pistons during a firing operation, it flows through suchbleed passageways into the portion of the cylinders, disposed on theside of the respetcive pistons remote from the aforementioned one sideat a high velocity. The velocity of such flow through the bleedpassageways is sufiiciently high that the heat caused by the friction ofthe gas passing therethrough is suflicient to create a serious problem,tending to distort the pistons, and tending to cause the pistons toseize in the cylinders. The pistons being in the interior of suchmachines, cooling thereof is difficult to achieve, and, therefore, suchheating of the pistons necessitates a slower rate of repeat firing ofthe machine than would be possible without the problem of overheating.It is a further object of the present invention to afford a novelmachine of the aforementioned type wherein the parts thereof are soconstituted and arranged that no heating, sufiicient to cause such aproblem, occurs.

Another object is to enable the equalizing of the pressures on theopposite sides of the driver pistons thereof to be accomplished in anovel and expeditious manner.

Another object is to afford a novel high-energy impact machine of theaforementioned type which is relatively small and compact in size, whilehaving a relatively high impact force capacity.

A further object is to afford a novel high-energy impact machine of theaforementioned type which is practical and efiicient in operation, andwhich may be readily and economically produced commercially.

Other and further objects of the present invention will be apparent fromthe following description and claims and are illustrated in theaccompanying drawings which, by way of illustration, show a preferredembodiment of the present invention and the principles thereof and whatwe now consider to be the best mode in which we have contemplatedapplying these principles. Other embodiments of the invention embodyingthe same or equivalent principles may be used and structural changes maybe made as desired by those skilled in the art without departing fromthe present invention and the purview of the appended claims. 9

In the drawings:

FIG. 1 is a front view, partly in cut-away section and partly schematic,illustrating a high-energy impact machine embodying the principles ofthe present invention;

FIG. 2 is a detail sectional view of the upper plate in the machineshown in FIG. 1 taken substantially along the line 2-2 in FIG. 1;

FIG. 3 is an enlarged detail sectional view taken substantially alongthe line 3-3 in FIG. 2;

FIG. 4 is an enlarged, fragmentary detail sectional view takensubstantially along the line 4-4 in FIG. 1;

FIG. 5 is a schematic view of the machine shown in FIG. 1 illustratingthe position of various parts thereof before charging;

FIG. 6 is a view similar to FIG. 5 illustrating the machine in chargedcondition;

FIG. 7 s a view similar to FIG. 5 illustrating the machine in cockedposition, wherein it is ready to be triggered for firing;

FIG. 8 is a view similar to FIG. 5 illustrating the machine in firedposition;

FIG. 9 is a schematic diagram of the hydraulic and gas circuits of themachine shown in FIG. 1; and

FIG. 10 is a schematic diagram of the electrical circuits of the machineshown in FIG. 1.

A machine 1, embodying the principles of the present invention is shownin the drawings to illustrate the presently preferred embodiment of thepresent invention. The machine 1 embodies, in general, an upright frame2 having two plates 3 and 4 slidably mounted in gibs 5 and 6 therein formovement toward and away from each other, two driver mechanisms 7 and 8being connected to the plates 3 and 4, respectively, for driving theplates 3 and 4 vertically along the gibs 5 and 6 toward each other, aswill be discussed in greater detail presently.

Only the one driver mechanism 8 will be discussed in detail, it beingunderstood that the driver mechanism 7 is identical thereto. Each of thedriver mechanisms 7 and 8 includes a cylinder 9 mounted on theprojecting upwardly from a respective end portion of the upper plate 3.The lower ends of the cylinders 9 extend downwardly into the upper plate3. A main chamber or high pressure chamber 10 extends between the lowerend portions of the cylinders 9 in the upper plate 3. The main chamber10 embodies four elongated, substantially cylindricalshaped compartments11, 12, 13, and 14 disposed in substantially parallel spaced relation toeach other, FIGS. 2 and 3, and each of the compartments 11-14 isconnected by a respective opening 15 into the lower end portion of eachof the cylinders 9. The outer ends of the compartments 1114 in the upperplate 3 are plugged to prevent the escape of gas therefrom.

Each of the driver mechanisms 7 and 8 also includes a driver piston 16reciprocably mounted in the cylinder 9 thereof. The driver pistons 16are sealingly and slidingly engaged with the side walls of therespective cylinders 9, and have respective mounting posts 17 connectedthereto and extending downwardly therefrom through the upper plate 3.The pistons 16 are adapted to seat on respective annular valve seats 18mounted in the lower end portions of the respective cylinders 9, whenthe pistons 16 are disposed in lowermost position in the cylinders 9.When the pistons 16 are disposed in such owermost position in thecylinders 9, an auxiliary chamber or triggering chamber 19 is definedwithin each valve seat 18 by the lower end of the respective cylinder 9and the lower face of the respective piston 16, FIG. 6. When the pistons16 are disposed in raised position in the cylinders 9, the chamber 10,the interior of the cylinders 9, and the triggering chambers 19 are indirect communication with each other. However, when the pistons 16 aredisposed in the aforementioned lowermost position in the cylinders 9,they are disposed in position to cover and close off the openings 15 andthereby said off communication of the main chamber 10 with the cylinders9 and the triggering chambers 19 through the openings 15.

The lower end of each of the posts 17 is connected to the lower plate 4by suitable connecting members 21 and 22, so that the lower plate 4 ismovable in the gibs 5 and 6 upwardly and downwardly relative to theupper plate 3 upon movement of the pistons 16 upwardly and downwardly,respectively, relative to the cylinders 9. Each of the posts 17 has anelongated passageway 23 extending longitudinally therethrough, the upperend of the passageway opening upwardly through the piston 16 into therespective cylinder 9. The lower end portions of the passageways 23 areconnected by respective trombone tubes 24, a passageway 25, a suitablecontrol valve 26, and a passageway 27 to a suitable source ofpressurized gas or pressurized elastic medium, such as, for example,pressurized nitrogen. The lower end portions of the passageways 23 areslidingly connected to the respective trombone tubes 24 by suitableseals 28 to thereby seal the connections between the posts 17 and thetrombone tubes 24 against leakage of gas therepast.

The main chamber 10 is disposed longitudinally in the upper plate 3 indownwardly spaced relation to the top face 29 of the plate 3, with thecompartments 11-14 disposed in horizontally spaced relation to eachother, FIGS. 2 and 3. The compartments 11 and 12, 12 and 13, and 13 and14 are spaced from each other by webs 30, 31, and 32, respectively.Another passageway 33 extends downwardly through the upper plate 3 fromthe upper face 29 thereof, FIGS. 2 and 4, the passageway 33 extendingdownwardly through the web 30 and terminating at its lower end in apassageway 34 extending longitudinally through the upper plate 3 indownwardly spaced relation to the chambers 10 and 19. Each of the endsof the passageway 34 is connected by a respective passageway 35extending upwardly therefrom and opening into the lower end of arespective cylinder 9 within the confines of the annular sea-t 18therein, to thereby interconnect each end of the passageway 34 with arespective one of the triggering chambers 19.

Another passageway 36 extends horizontally across the passageway 33 fromone side wall 37 of the top plate -3 and terminates at its inner endsubstantially vertically above the compartment 12 of the main chamber10, FIG. 4. The inner end of the passageway 36 interconnects with theupper end portion of a passageway 38 which extends downwardly throughthe plate 3 from the upper face 29 thereof, and terminates at its lowerend in direct communication with the compartment 12, FIG. 4.

A valve seat 39 is mounted in the passageway 38 between theinterconnection of the latter with the passageway 36 and the compartment12, and a poppet valve 40 is slida-bly mounted in the valve seat 39 forvertical movement between seating engagement with the valve seat 39 andspaced relation thereto, as shown in solid and broken lines,respectively, in FIG. 4, to thereby close and open the passageway 38.The valve 40 is effective to control the triggering of the machine 1 forfiring, as will be discussed in greater detail presently.

A hydraulically operated actuator 41 is mounted on the frame 2 above thevalve 40 in position to actuate the latter, FIGS. 1 and 4. The actuator41 includes a housing 42 having an upright cylinder 43 disposed abovethe valve 40 in vertical alignment therewith, and a piston 44reciprocably mounted in the cylinder 43 for movement upwardly anddownwardly therein, into and out of the housing 42. Two hydraulic lines45 and 46 are connected into the upper and lower end portions of thecylinder 43, and are connected through suitable valving to a suitablesource of hydraulic fluid, as will be discussed in greater detailpresently, for feeding hydraulic fluid under pressure into the upper endlower end portions of the cylinder 43 and thereby force the piston 44downwardly and upwardly, respectively. Downward movement of the piston44 is effective to push the poppet valve 40 into open position, andupward movement of the piston 44 is effective to permit the poppet valve40 to move upwardly into closed position.

The upper end portion of the passageway 33 is connected to a trombonetube 47 which is mounted on and projects downwardly from the upperportion of the frame 2, FIG. 4. The passageway 33 is slidingly connectedto the trombine tube 47 by a suitable seal 51 to prevent the leakage ofgas therebetween, and the upper end portion of the trombone tube 47 isconnected by a passageway 48, a valve 49, and a passageway 50 to thepassageway 25 and, therefore, the valve 26, FIG. 1. It will beremembered that the valve 26 is connected to a suitable source ofpressurized gas, and, therefore, it will be seen that when the valves26, 49, and 40 are open, passageways 23, 25, 50, 48, 33, 36 and 38afford passageways for simultaneously feeding gas from said source intothe cylinders 9 and the chambers 10 and 19 irrespective of the positionof the pistons 16 in the cylinders 9. Thus, with the valves 26, 49, and40 open, the entire gas circuit for firing the machine 1 may be filledwith pressurized gas from the gas source connected to the valve 26 asillustrated diagrammatically in FIG. 9.

In the preferred form of the machine shown in the drawings, the outerend of the passageway 36 extends through the side wall 37 of the upperplate 3 to facilitate the formation of the passageway 36 in the plate 3,and is plugged by a suitable plug 52, the connection between the valve49 and the passageway 33 being made through the trombone tube 47 and thepassageway 48. However, as will be appreciated by those skilled in theart, if desired, the connection between the valve 49 and the passageway33 may be made through the outer end of the passageway 36, the plug 52being removed for such purposes, and, in that event, the upper end ofthe portion of the passageway 33 above the passageway 36 would besuitably closed such as, for example, by a suitable plug, not shown.

The valve 49 is preferably of the same construction as the trigger valvemechanism 39-41, embodying a poppet valve 53 which is movable into andout of engagement with a valve seat 54, and embodying a hydraulicallyoperated actuator 55 which is identical in construction to the actuator41, as illustrated diagrammatically in FIG. 9. In the operation of themachine 1 the opening and closing of the valves 40 and 49 is controlledby the actuators 41 and 55, as will be discussed in greater detailpresently.

Two compensating or counter balancing units 56 are mounted at respectiveends of the upper plate 3 for supporting the latter against the force ofgravity, FIGS. 1 and 9. Each of the counter balancing units includes acylinder 57 connected to the frame 2 in depending relation thereto abovethe upper plate 3, and has a piston 58 sealingly and slidably mounted inthe cylinder 57 and connected to the upper plate 3 by a piston rod 59extending downwardly through the cylinder 57. The cylinder 57 of each ofthe counter-balancing units '56 is filled with compressed gas below theproton 58 therein so that the force of the compressed gas is such as toovercome the force of gravity on the plate 3. The counter-balancingunits 56 are also effective to return the upper plate 3 to raisedposition after a firing of the machine 1, as will be discussed ingreater detail presently.

Each of the driver mechanisms 7 and 8 also includes a floating piston 60sealingly and slidably engaged in the cylinder 9 thereof above thepiston 16 in that cylinder. The floating piston 60 is preferablycup-shaped both upwardly and downwardly, having an upwardly openingconcavity 61 and a downwardly opening concavity 62 therein FIG. 1. Thefloating pistons 60 in the driver mechanisms 7 and 8 are reciprocablelongitudinally of the cylinders 9 between a fully raised position, asshown in FIGS. 1 and 5, and a fully lowered position as shown in FIG. 6.

Two tubes 63 are threaded into the upper ends of respective ones of thecylinders 9, and project upwardly through the upper end of the frame 2into vertically extending cylinders 64 mounted thereon. Each of thetubes 63 includes a guide piston 65 sealingly and slidingly engaged withthe side walls of a guide cylinder 66 mounted in the respective cylinder64. The guide cylinders 66 are sealed at their lower ends to therespective cylinders 64 in which they are mounted, and above the lowerends are spaced radially inwardly therefrom, terminating at their upperends in downwardly spaced relation to the upper ends of the respectivecylinders 64. Suitable conduits, such as pipes 68 are connected to thelower end portions of the cylinders 64 above the seals 67 for feedinghydraulic fluid into the guide cylinders 64, the fluid thus fedinto thecylinders 64 flowing upwardly through the passageways 69 defined by theradially spaced portions of the cylinders 64 and 66, and then downwardlythrough the tubes 63 into the cylinders 9 above the floating pistons 60.The conduits 68 are connected through suitable controls to a suitablesource of pressurized hydraulic fluid for feeding hydraulic fluid intoand out of the cylinders 9 above the floating pistons 60, as will bediscussed in greater detail presently.

In FIGS. 58 of the drawings various steps in the operation of themachine 1 are diagrammatically illustrated. Thus, for example, ininitially preparing the machine 1 for operation, the valves 26, 40, and49 may all be opened and a suitable pressurized elastic medium, such as,for example, compressed nitrogen may be fed from a suitable gas sourcethrough the valves 26, 40, 49 into the cylinders 9 and the chambers 10and 19 to thereby completely fill the gas circuit of the machine 1 withthe pressurized gas, as illustrated in FIG. 5, and the valve 26 may thenbe closed.

After the gas circuit of the machine 1 has thus been filled with gas tothe desired proper pressure, the pistons 60 may be moved downwardly inthe cylinders 9 by hydraulic fluid pressure applied to the upper facesof the pistons 60. This downward movement of the floating pistons 60 iseffective to move the pistons 16 downwardly into seating engagement withthe annular seats 18 and to compress all of the gas in the machine 1 toa high pressure, as illustrated in FIG. 6.

Thereafter, the triggering valve 40 is closed by means which will bedescribed in greater detail presently, to thereby close offcommunication between the main chamber 10 and the triggering chambers19. With the valve 49 remaining open the hydraulic fluid above thefloating piston 60 is then released to sump, permitting the floatingpistons 60 to move upwardly in the cylinders 9. During this movement ofthe pistons 60, the pressurized gas in the passageways 36, 33, 34, 35,48, 5t), 25 and 23, the triggering chambers 19, and the valve 49 expandinto the cylinders 9 above the driver pistons 16, and the pressurethereof equalizes throughout this portion of the gas circuit at arelatively low pressure as compared to the pressure in chamber 10, asillustrated in FIG. 7.

In this connection it will be noted that during both charging andventing of the machine 1, FIGS. 6 and 7, gas is trapped between thepistons 60 and the pistons 16, which is substantially at the samepressure as the gas in the triggering chambers 19. Because of thegreater area of the pistons 16 subjected to the pressure of gas betweenthe pistons 16 and the floating pistons 60, as compared to the area ofthe pistons 16, subjected to the pressure of gas in the triggeringchambers 19, the gas pressure above the pistons 16 retains the pistons16 in seated relation to the annular seats 18 during the aforementionedupward movement of the floating pistons 60. When, during theaforementioned upward movement of the pistons 60, they reach their fullyraised positions, as shown in FIG. 7, the valve 49 is closed, and,therefore, at this stage of the operation of the machine 1, the mainchamber 10 is pressurized to a high pressure, the valve 40 remainingclosed, and the remainder of the gas circuit of the machine 1 is at thelow pressure, so that the machine 1 is in cocked condition ready to betriggered for firing.

In the firing of the machine 1, the valve 40 is moved into openposition. The opening of the valve 40 permits high pressure gas to flowfrom the main chamber through the passageways 38, 36, 33, 34, and 35into the triggering chambers 19 to substantially instantaneously subjectthe lower faces of the driver pistons 16 and the lower ends of thecylinders 9 to the full pressure of the main chamber 10, and therebyquickly unseat the driver pistons 16 and uncover the openings connectingthe cylinders 9 to the main chamber 10. The uncovering of the openings15 permits high pressure gas to flow therethrough from the main chamber10 into the cylinders 9 below the pistons 16, and thereby continues tosubject the lower faces of the driver pistons 16 and the lower ends ofthe cylinders 9 to the full pressure of the main chamber 10, as thepistons 16 and lower ends of the cylinders 9 are accelerated away fromeach other. The force of the gas thus released into the cylinders 9 fromthe main chamber 10 causes the driver pistons 16 to be acceleratedupwardly at a high rate, and causes the cylinders 9 to be accelerateddownwardly at a high rate. The acceleration of the driver piston 16 andthe cylinders 9 causes the lower plate 4 and the upper plate 3,respectively, to be likewise accelerated, and brings the plates 3 and 4together at a relatively high impact speed. The movement of the plates 3and 4 toward each other is effective to cause die parts 63 and 64carried thereby to be brought together in the same manner, to therebyperform a forming action on a piece of metal, not shown, placedtherebetween.

A machine constructed according to the construction shown herein mayoperate on less than ten-second cycles and may deliver as much as145,000 foot pounds of energy where the weight of the plates 3 and 4 areapproximately 4800 pounds each and where normal operating gas pressureis 1500 pounds per square inch, with the plates having a combined strokeof twelve inches.

Referring now primarily to FIGS. 9 and 10', in the operation of themachine 1 the selector switch SS-l, FIG. 10, may first be closed tothereby operatively connect the power lines 70 and 71 to a suitablesource of electric power 72. Thereafter, the two push button switchesPB1 and PB-2 may be closed to thereby energize the two motors 73 and 74,respectively. The motors 73 and 74 may be connected to suitablehydraulic pumps, not shown, affording the high pressure oil source 75,FIG. 9, for feeding hydraulic fluid under pressure through the lines 79and 81, respectively, of the machine 1. The closing of the push buttonswitches PB-l and PB-2 are also effective to energize the holding relaycoils HR-l and HR-2 to thereby close the normally open relay contactsHR-l' and HR2, respectively, and thus afford holding circuits effectiveto maintain energization of the motors 73 and 74 until the push bottonswitches PB-3 and PB-4 are moved into open position to thereby open thecircuits to the motors 73 and 74 and the holding relays HR-l and HR2.When the motors 73 and 74 are thus energized, the incandescent lamps 76and 77 are illuminated to thereby indicate that the motors 73 and 74 arerunning and hydraulic pressure is available for the hydraulic circuit ofthe machine.

The actuators 41 and 55 for the valves 40 and 49, respectively, areoperatively connected to solenoid valves SV2 and SV4, respectively, FIG.9, for controlling the operation thereof. The solenoid valve SV2 isconnected by a hydraulic line 80 to a high pressure hydraulic line 81connected to the high pressure oil source 75. The solenoid valve SV2 isalso connected by the two hydraulic lines 45 and 46 to the upper andlower ends of the cylinder 42 of the actuator 41. The solenoid valve SV2is so constructed that when it is not energized, hydraulic fluid is fedunder pressure through the line 45 into the actuator 41 to thereby forcethe piston 44 thereof downwardly and move the valve 40 into openposition, the hydraulic fluid below the piston 44 being fed through theline 46 and the valve SV2 to sump 82. Energization of the solenoid valveSV2 is effective to reverse the connections of the lines 45 and 46, theline 46 then being connected to the high pressure hydraulic line 81, andthe line 45 then being connected to sump 82, to thereby move the piston44 upwardly in the actuator 41 and permit the valve 40 to move upwardlyinto closed position.

The solenoid valve SV4 is connected between the high pressure hydraulicline 81 and the actuator 55 for the valve 49 in a reverse manner fromthat in which the solenoid valve SV2 is connected between the hydraulicline 81 and the actuator 41, FIG. 9. The valve SV-4 is connected by aline 84 to the hydraulic line 81, and by two lines and 86 to the bottomand top, respectively, of the actuator 55. Energization of the solenoidvalve SV4 is effective to cause hydraulic fluid to flow from the line 81through the line 86 to the upper portion of the actuator 55, and permithydraulic fluid to flow from the bottom portion of the actuator 55through the line 85 to sump 82. Thus, energization of the solenoid valveSV4 is effective to so actuate the actuator 55 that the valve 49 isopened thereby. When the solenoid valve SV-4 is not energized it iseffective to reverse the connections of the lines 85 and 86, the line 85then being connected to the high pressure line 81, and the line 86 thenbeing connected to sump 82 to thereby move the piston of the actuator 55upwardly therein and permit the valve 49 to move into closed position.

Thus, it will be seen that after operation of the motors 73 and 74 hasbeen initiated in the aforementioned manner, so that hydraulic fluidunder pressure is present in the hydraulic line 81, and with both of thesolenoid valves SV2 and SV-4 deenergized, the actuator 41 is effectiveto open the triggering valve 40, and the actuator 55 is effective topermit the vent valve 49 to close. If, at this time, the gas circuit ofthe machine 1 has not been initially charged with low pressure gas, orit is desired to feed additional gas into the gas circuit of the machine1, these things may now be accomplished by opening the valve 49 and thevalve 26. Opening of the valve 49 may be accomplished by closing theselector switch SS-3, FIG. 9, to thereby energize the valve SV4 and thuscause the actuator 55 to move the valve 49 into open position. The valve26 may then be opened to permit the flow of gas through the valves 40and 49 into the gas circuit of the machine 1, the pressure equalizingthroughout the gas circuit, as illustrated in FIG. 5, as previouslydescribed. When the gas circuit has been pressurized to the desiredpressure, the valve 26 may be closed to stop the flow of gas thereinto.Thereafter, the selector switch SS-3 may again be moved into openposition, to thereby deenergize the solenoid valve SV-4 and permit thepiston in the actuator 55 to move upwardly and thus permit the valve 49to be closed by the pressure of the gas in the passageway 48.

The machine 1 is then in condition to be charged with high pressure gas.This may be accomplished by moving the selector switch SS-2, FIG. 10,from stop to run position and then closing the charge push button switchPB-S. The closing of the push button switch PB-5 energizes the controlrelay CR-l to thereby close the normally open relay contacts CR1' toafford a holding circuit around the push button switch PB-5, which maythen be permitted to move to open position. The energization of theholding relay CR-l also closes the normally open relay contacts CR1",which energizes the solenoid valve SV-l, FIG. 10. The solenoid valveSV-l may be embodied in the control panel 78, and the energizationthereof is effective to connect the hydraulic line 79 to the highpressure oil source 75, FIG. 9. The hydraulic line '79 is connected tothe lines 68, which are connected to the cylinders 64, FIGS. 1 and 9,and, therefore, when the solenoid valve SV-l is energized,

9 hydraulic fluid is fed under pressure through the lines 69, thecylinders 64, and the tubes 63 into the cylinders 9 above the floatingpiston 60 to thereby move the pistons 60 downwardly from the positionshown in FIG. into the position shown in FIG. 6.

During this movement of the floating pistons 60 downwardly, the valve 40remains open, the solenoid valve SV-2 not being energized. Also, duringthe initial movement of the pistons 60 downwardly the valve 49 remainsclosed, the solenoid valve SV-4 not being energized.

However, a pressure switch PS-2 is connected to the hydraulic line 79,and is effective to cause the solenoid SV-4 to be energized, to therebyopen the valve 49 so that the passageways between the triggeringchambers 19 and the cylinders 9 above the pistons 16 are open to permitcharging of the entire gas circuit with high pressure gas, illustratedin FIG. 6. The pressure switch PS-2 is such that when the pressure inthe hydraulic line 79 is below a relatively high pressure, such as, forexample, 1800 pounds per square inch, the pressure switch contacts PS-Zthereof, FIG. 10, are disposed in open position, and when the pressurein the line 79 exceeds the aforementioned 1800 pounds per square inchthe pressure switch PS2 is effective to close the contacts PS2. Thus,during a charging operation, as the pressure in the hydraulic line 79'rises to thereby force the floating pistons 16 downwardly, the pressureswitch PS-Z is actuated when the pressure in the line 79 exceeds 1800pounds per square inch, and the pressure switch contacts PS-Z' arethereby closed. The closing of the contacts PS2' energizes the controlrelay CR-2, the circuit for the relay CR-2 extending through thenormally closed relay contacts CR-3". The energization of the relay CR-2closes the normally open relay contacts CR-2' to thereby afford aholding circuit for the relay CR-2 around the pressure switch contactsPS-Z'. The energization of the control relay CR2 also closes thenormally open relay contacts CR-Z", which energizes the solenoid valveSV-4 and opens the valve 49 to thus permit the charging pressure toequalize throughout the gas circuit as illustrated in FIG. 6.

At the completion of the downward movement of the floating pistons 60,the driver pistons 16 are disposed in seating engagement with theannular seats 18, and the entire gas circuit of the machine 1 is chargedwith high pressure gas, as shown in FIG. 6.

Thereafter, a stroke push button switch PB-6 may be actuated, whichenergizes solenoid valve SV-2, the circuit for solenoid valve SV-Zextending through the normally closed relay contacts CR-3'. Theenergization of the solenoid valve SV-2 is effective to permit the valve40 to be closed by the gas pressure in the passageway 38, as previouslydescribed, to thereby close communication between the main chamber 10and the triggering chambers 19.

The actuation of the stroke push button switch PB-6 is also effective toenergize the timer relay TR1 and the warning lamp 83, the circuit fordoing so extending through the aforementioned normally closed relaycontacts CR-3'. The energization of the timer relay TR-l closes thenormally open relay contacts TR-l' to thereby afford a holding circuitfor the timer relay TR-l, the solenoid valve SV-2 and the warning lamp83, around the push button switch PB-6.

The energization of the timer relay TR-l also closes the normally openrelay contacts TR-l". However, the contacts TR-l" are delayed closingcontacts, the timing of which is such that they do not close until afterthe trigger valve 40 has seated. The closing of the contacts TR-l"energizes valve windings SV-S, FIG. 10. The valve windings SV-3 are onthe same valve as the valve windings SV-l, and the actuation of thestroke push button switch PB-6 opened the circuit to the valve windingsSV-l and thereby deenergized the latter. Therefore, the energization ofthe windings SV-3 actuates the solenoid valve SV-l to a position whereinthe cylinders 64 are connected through the hydraulic lines 68 and 79 andthe solenoid valve SV-1 to sump to thereby permit the hydraulic fluidabove the floating pistons 60 to flow to sump, the gas pressure beneaththe floating pistons 60 moving the latter upwardly into fully raisedposition in the cylinders 9.

It will be remembered that energization of the solenoid valve SV-lcaused by closing of the charge push button PB-S, and the consequentenergization of the control relay CR-l, caused the hydraulic line 79 tobe pressurized. A pressure switch PS-l is connected to the hydraulicline 79 and is operable upon the pressure in the line 79 exceeding asuitable predetermined pressure, such as, for example, 35 pounds persquare inch, to open pressure switch contacts PS-l'. Therefore, whilethe pressure in the line 79 exceeds 35 pounds per square inch a circuitthrough the timer relay contacts TR-l' to the control relay CR-3 remainsopen. The exhausting of the hydraulic fluid from the hydraulic line 79and from the cylinders 9 above the pistons 60, and the consequentrelieving of the pressure in the hydraulic line 79 by the aforementioneddeenergization of the solenoid valve SV- 1 and the energization of thevalve windings SV-3 causes the pressure in the line 79 to drop below theaforementioned 35 pounds per square inch so that the contacts PS-l' ofthe pressure switch PS-l again move the closed position.

The closing of the pressure switch contacts PS-l, caused'by the drop ofpressure in the line 79, energizes the control relay CR3, which opensthe normally closed relay contact CR-3', and thereby deenergizes thesolenoid valve SV-2, the warning lamp 83, and the timer relay TR1. Theenergization of the control relay CR-3 also opens the normally closedrelay contacts CR-3" and thereby opens the holding circuit for thecontrol relay CR2 and thereby deenergizes the latter.

The deenergization of the control relay CR-Z opens the normally openrelay contacts CR-Z" and -deenergizes the solenoid valve SV-4. Thedeenergization of the solenoid valve SV-4 causes the lower end of theactuator 55 to be connected through the hydraulic line to thepressurized hydraulic line 81, and causes the upper end portion of theactuator 55 to be connected to the hydraulic line 85 to sump 82, tothereby cause the valve 49 to close, so that the machine 1 is now readyto be fired in the preferred manner.

The aforementioned deenergization of the solenoid valve SV-2 caused bythe drop in pressure in the hydraulic line 79 below 35 pounds per squareinch, and the consequent opening .of the relay contact CR-3 causes thevalve SV-2 to connect the hydraulic line 45 to the high pressurehydraulic line 81 to thereby force the piston 44 of the actuator 41downwardly and thus move the trigger valve 40 to open position. Theopening of the trigger valve 40 triggers the firing of the machine 1,the high pressure gas in the main chamber 10 flowing from the mainchamber 10 past the valve 40 and through the passageways 36, 33, 34, and35 into the triggering chambers 19 to thereby substantiallyinstantaneously subject the lower faces of the driver pistons 16 and thelower ends of the cylinders 9 to the full pressure of the gas in themain chamber 10. This causes the driver pistons 16 and the lower ends ofthe respective cylinders 9 to be rapidly accelerated away from eachother, and the consequent uncovering of the openings 15 permits the highpressure gas in the main chamber 10 to continue to rush into thecylinders 9 below the lower faces of the driver pistons 16 and continueto subject the spaces between the lower faces of the driver pistons 16and the lower ends of the cylinders 9 to the full pressure of the mainchamber 10, as the pistons 16 and lower ends of the cylinders 9 areaccelerated away from each other. The force created by the flow of gasfrom the main chamber 10 into the cylinders 9 causes the driver pistons16 to be rapidly accelerated upwardly, and likewise causes the cylinders9 to be rapidly accelerated downwardly. Such movement of the pistons 16and the cylinders 9 causes corresponding movement of the lower plate 4and the upper plate 3, respectively, to thereby bring the plates 3 and4, and the die parts 63 and 64 carried thereby, respectively, intocontact with each other with a high impact force.

The deenergization of the timer relay TR1, caused by the opening of thepressure switch contacts PS-1' upon the drop in pressure in the line 79below 35 pounds per square inch, and the consequent opening of the relaycontact CR-3' caused the timer relay contacts TR-l to again open, thusopening another portion of the circuit to the control relay CR3. Thedeenergization of the timer relay TR1 also caused the timer relaycontacts TR1 to open and thereby deenergize the windings SV3 on thesolenoid valve SV1. Therefore, if the stroke push button PB6 is thenreleased to thereby close the circuit to the solenoid valve SV-l, a newcycle of operation of the machine 1 is commenced, the charging circuitthrough the control relay CR-l remaining closed because of the holdingcircuit through the relay contacts CR-l'.

In such a new cycle of operation the release of the stroke push buttonswitch PB6 commences a new charging operation, and after charging of themachine with high pressure gas is completed, as illustrated in FIG. 6,the stroke button switch PB-6 may again be actuated to again cause theventing operation, as illustrated in FIG. 7, and the firing operation,as illustrated in FIG. 8, to again be performed as previously described.Thus, it will be seen that in the machine 1 the gas used for actuationof the driver mechanism thereof is embodied in a closed circuit, and nonew gas need be fed into the machine between cycles of operationthereof.

The machine 1 also includes a shut-down push button switch 87, FIG. 10,which may be actuated by the operator when it is desired to shut downoperation of the machine 1. Actuation of the push button switch 87 fromits normal position shown in FIG. 10 restores the machine 1 to thecondition in which it was prior to the initial actuation of the chargepush button switch PBS, even if the machine 1 has been charged. Suchactuation of the shut-down switch 81 opens the circuit through theholding relay contacts CR-l' and thereby deenergizes the relay CR-l.This makes actuation of the charge button switch PBS necessary to againinitiate operation of the machine 1.

The actuation of the shut-down push button switch 87 also closes thecenter contacts thereof to thereby energize the solenoid valve SV3, andin addition closes the lower contacts thereof to thereby energize thecontrol relay CR-3 and thus open the normally closed relay contactsCR-3'. The energization of the solenoid valve SV-3 causes the hydraulicfluid in the cylinder 64 to drain to sump. The opening of the normallyclosed contacts CR-3 insures that the solenoid valve SV2 is deenergizedso that no hydraulic pressure is present in the actuator 41 below thepiston 44 thereof and the trigger valve 40 is disposed in open position.The latter insures that no gas is trapped in the main pressure chamber10 for accidentally firing the machine.

Thereafter, to complete shutting down of the machine 1, the operator mayactuate push button switches PB-3 and PB4, FIG. 10, to thereby open thecircuits to HR-l and HR-2, respectively, and thereby deenergize themotors 73 and 74. The deenergization of the holding relays HR1 and HR2makes it necessary to actuate the push button switches PB-l and PBZ whenit is again desired to start the machine 1 in operation.

It will be remembered that in the operation of the machine 1 shown inthe drawings, the vent valve 49 is closed during firing of the machine.This closes the passageway 48-50 and thereby prevents the flow of gasfrom the main chamber 10 through the passageways 48, 50, 25, and 23 intothe cylinders 9 above the pistons 16. The vent valve 49 remains closedafter firing until the next charging operation of the machine, when thepressure in the hydraulic line 79 builds up to over 1800 pounds persquare inch.

If desired, the machine 1 may be constructed without the vent valve 49being embodied therein, the passageways 48 and 50 then being connecteddirectly to each other. The valve 49 in the preferred embodiment of themachine 1 shown in the drawings serves the highly useful purpose ofpreventing high pressure gas from flowing through the driver pistons 16during firing of the machine 1, and thereby prevents the heating whichwould otherwise occur from the flow of gas through the pistons 16.However, in a machine constructed in accordance with the principles ofthe present invention, the passageways extending from the trombone tubes24 in the driver piston 16 to the passageway 33 in the upper plate 3 mayreadily be disposed outside of the machine 1 so that they are readilyaccessible for efficiently cooling of the gas passing therethrough.Thus, even if the valve 49 were eliminated from the machine 1, themachine 1 would afford a novel construction which eliminates asubstantial portion of the disadvantages heretofore caused by thepassage of gases through driver pistons during the firing of high-energyimpact machines.

From the foregoing it will be seen that the present invention affords anovel high-energy impact machine which may be charged, vented, and firedin a novel and expeditious manner.

Also, it will be seen that the present invention affords a novelhigh-energy impact machine, the entire gas circuit of which may befilled with gas from an outside source irrespective of whether or notthe driver pistons thereof are unseated from the annular seats therefor.

In addition, it will be seen that the present invention affords a novelhigh-energy impact machine which does not require the recharging of anyportion of the gas circuit thereof between successive cycles ofoperation, and wherein the time between such successive cycles ofoperation may be extremely small.

Thus, while we have illustrated and described the preferred embodimentof our invention, it is to be understood that these are capable ofvariation and modification, and we therefore do not wish to be limitedto the precise details set forth, but desire to avail ourselves of suchchanges and alterations as fall within the purview of the followingclaims.

We claim:

1. A high-energy impact machine comprising (a) a pair of plates movabletoward and away from each other,

(b) a first of said plates having a cylinder and two chambers therein,

(c) said chambers and cylinder intersecting each other,

(d) a driver piston (1) slidably mounted in said cylinder and (2) having(a') a first end face facing toward one of said chambers and (b) anopposite second end face facing into said cylinder,

(e) a seat member extending around and defining the outer periphery ofsaid one chamber disposed in position to engage said piston to cut offdirect communication between said one chamber and both said cylinder andthe second of said chambers,

(f) a post attached to said piston and to the second of said plates,

(g) means for supplying gas under pressure to said second chamber, and

(11) means for feeding said gas under pressure from said second chamberto said first chamber to thereby move said piston off said seat toexpose said first face to the pressure in said second chamber andthereby 1 3 force said cylinder and piston in opposite directions andthereby move said plates toward each other.

2. A high-energy impact machine comprising (a) a pair of plates movabletoward and away from each other,

(b) a first of said plates having (1) a cylinder and two chamberstherein, and

(2) a passageway therein extending between said chambers,

(c) said chambers and cylinder intersecting each other,

(d) a driver piston (1) slidably mounted in said cylinder and (2) having(a) a first end face facing toward one of said chambers and (b') anopposite second end face facing into said cylinder,

(e) a seat member extending around and defining the outer periphery ofsaid one chamber disposed in position to engage said piston to out offdirect communication between said one chamber and both said cylinder andthe second of said chambers.

(f) a post attached to said piston and to the second of said plates,

(g) means for supplying gas under pressure to said second chamber, and

(h) valve means for closing and opening said passage- .way to thereby,respectively,

(1) prevent the flow of gas through said passageway from said secondchamber to said first chamher, and

(2) permit the flow of gas through said passageway from said secondchamber to said first chamber to thereby force said piston off said seatto expose said first face to the pressure in said second chamber andthereby force said cylinder and piston in opposite directions andthereby move said plates toward each other.

5 3 A high-energy impact machine as defined in claim 2, and in which'(a) said'valve means includes a poppet valve mounted in said one plateand movable into open and closed position in said passageway.

4. A high-energy impact machine as defined in claim (a) in which saidpiston and post have a second passageway extending therethrough,

(b) which includes (1) a third passageway extending between saidfirst-mentioned passageway and said second passageway, and

(2) other valve means for opening and closing said third passageway, and

'(c)-in which said first-mentioned valve means are disposed between saidthird passageway and said second chamber. 5. A high-energy impactmachine as defined in claim 4,

and in which (a) said first-mentioned valve means includes a poppetvalve mounted in first-mentioned passageway,

(b) said third passageway extends through a portion of said first plateand connects to said first-mentioned passageway therein, and

(c) said poppet valve is movable into open and closed position tothereby open and close communication through said first-mentionedpassageway between said second chamber and both said first chamber andsaid third passageway.

6. A high-energy impact machine comprising (a) first and second movableplates adapted to be simultaneously accelerated toward each other by anacceleration force,

(b) a source of a confined pressurized elastic medium,

(0) a cylinder on said first plate having connection with said sourcefor substantially instantaneously releasing said pressurized elasticmedium from said source into said cylinder, (d) said cylinder having twoends, (e) a driver piston in sealing and slidable contact with the sidewalls of said cylinder, (f) said driver piston (1) having opposite endfaces facing toward respective ends of said cylinder, (2) beingoperatively connected to said second plate, and (3) being reciprocablelongitudinally of said cylinder between (a) one position adjacent oneend of said cylinder effective to close said connection, and (b')another position wherein said connection is disposed between said oneend and the one of said faces facing said one end to thereby open saidconnection, and (g) means for feeding pressurized elastic medium fromsaid source to between said one end and said one face when said pistonis disposed in said one position to thereby move said piston to saidother position and thereby open said connection and substantiallyinstantaneously release said pressurized elastic medium through saidconnection fromsaid source into said cylinder to act on said one end andsaid one face to provide an acceleration force to simultaneouslyaccelerate said piston and cylinder in opposite directions and saidplates toward each other. 7. A high-energy impact machine comprising (a)first and second movable plates adaptedto be simultaneously acceleratedtoward each other by an acceleration force, (b) a source of a confinedpressurized elastic medium in said first plate, (c) a cylinder on saidfirst plate having connection with said source for substantiallyinstantaneously Y releasing said pressurized elastic medium from saidsource into said cylinder, (d) said cylinder having two ends, (e) one ofsaid ends facing toward said second plate, (f) a driver piston insealing and slidable contact with the side walls of said cylinder, (g)said driver piston (1) having opposite 'end faces facing towardrespective ends of said cylinder, (2) being operatively connected tosaidv second plate, and (3) being reciprocable longitudinally of saidcylinder between (a) one position adjacent said one end of said cylindereffective to close said connection, and t (b') another position whereinsaid connection is disposed between said one end and the one face facingsaid one end to thereby open said connection, and (h) means in saidfirst plate for feeding pressurized elastic medium from said source tobetween said one end and said one face when said piston is disposed insaid one position to thereby move said piston to said other position andthereby open said connection and substantially instantaneously releasesaid pressurized elastic medium through said connection from said sourceinto said cylinder to act on said one end and said one face to providean acceleration force to simultaneously accelerate said piston andcylinder in opposite directions and said plates toward each other. a 8.A high-energy impact machine comprising (a) first and second movableplates adapted to be simultaneously accelerated toward each other by anacceleration force, (b) a chamber in said first plate for holding asupply of a pressurized elastic medium,

15 (c) a cylinder in said first plate having two oppositely disposedends, (d) one of said ends facing toward said second plate, (e) saidcylinder having an opening through the side wall thereof adjacent saidone end and in communication with said chamber for substantiallyinstantaneously releasing said pressurized elastic medium from saidchamber into said cylinder, (f) a driver piston in sealing and slidablecontact with the side walls of said cylinder, (g) said driver piston (1)having opposite end faces facing toward respective ends of saidcylinder, (2) being operatively connected to said second plate, and (3)being reciprocable longitudinally of said cylinder between (a') oneposition adjacent said one end of said cylinder effective to cover andclose said opening, and (b') another position wherein said opening isdisposed between said one end and the one face facing said one end, (h)a passageway in said first plate connected into said chamber and saidone end of said cylinder for feeding said pressurized elastic mediumfrom said chamber into said cylinder between said one end and said oneend face when said piston is disposed in said one position to therebymove said piston to said other position and thereby substantiallyinstantaneously release said pressurized elastic medium though saidopening from said source into said cylinder to act on said one end andsaid one face to provide an acceleration force to simultaneouslyaccelerate said piston and cylinder in opposite directions and saidplates toward each other, and (i) valve means in said passageway foropening and closing the latter. 9. A high-energy impact machine asdefined in claim 8, and which includes (a) another passageway (1)connected at one end to said first-mentioned passageway on the side ofsaid valve means remote from said chamber, and (2) connected at theother end to the interior of said cylinder disposed between the otherend thereof and the other end of said piston. 10. A high-energy impactmachine as defined in claim 9, and which includes (a) valve means insaid other passageway for opening and closing the latter. 11. Ahigh-energy impact machine as defined in claim 10, and in which (a) saidother passageway includes trombone tubes mounted in said first andsecond plates. 12. A high-energy impact machine comprising (a) first andsecond movable plates adapted to be simultaneously accelerated towardeach other by an acceleration force, (b) a chamber in said first platefor holding a supply of a pressurized elastic medium, (c) two cylindersmounted in said first plate in substantially parallel spaced relation toeach other, (d) each of said cylinders (1) having two oppositelydisposed ends with one of said ends facing toward said second plate, and(2) having passage means through the side wall thereof adjacent said oneend and in communication with said chamber for substantiallyinstantaneously releasing said pressurized elastic medium from saidchamber into said cylinder, (e) two driver pistons, (f) each of saiddriver pistons,

(1) being in sealing and slidable contact with the side walls of arespective one of said cylinders, (2) being operatively connected tosaid second plate, (3) having opposite end faces facing towardrespective ends of said respective cylinder, and (4) being reciprocablelongitudinally of said respective cylinder between (a') one positionadjacent said one end of said respective cylinder effective to closesaid passage means, and (b') another position wherein said passage meansare disposed between said one end and the one face of said respectivepiston facing said one end to thereby open said passage means in saidrespective cylinder, and (g) means for simultaneously feedingpressurized elastic medium from said chamber into both of said cylindersbetween said one ends and said respective one faces when said pistonsare disposed in said one position to thereby simultaneously move both ofsaid pistons to said other position and thereby open said passage meansin both cylinders and substantailly instantaneously release saidpressurized elastic medium from said chamber simultaneously into both ofsaid cylinders to simultaneously act on said one end of both of saidcylinders and said one face of both of said pistons to provide anacceleration force to simultaneously accelerate said pistons and saidcylinders in opposite directions and said plates toward each other. 13.A high-energy impact machine as defined in claim 12 and in which (a)said chamber comprises a plurality of elongated compartments extendingthrough said one plate between said cylinders and connected to both ofsaid cylinders by said passage means. 14. A high-energy impact machineas defined in claim 13, and in which (a) said means includes (1) anelongated passageway extending through a portion of said first plate andconnected between one of said compartments and said one end of both ofsaid cylinders, and (2) valve means in said passageway for opening andclosing said passageway to thereby control the flow of said mediumtherethrough from said one compartment to said cylinders. 15. Ahigh-energy impact machine as defined in claim 14, and which includes(a) a second passageway (1) extending through said pistons and a portionof said one plate, and (2) operatively connected to said elongatedpassageway on the side of said valve means remote from said onecompartment for interconnecting said elongated passageway and theinterior of said cylinders on the side of said pistons remote from saidsecond plate, and (b) valve means in said second passageway for openingand closing the latter.

for feeding pressurized elastic medium References Cited UNITED STATESPATENTS 8/1961 Ottestad 73-12 6/1964 Ottestad 72-453

1. A HIGH-ENERGY IMPACT MACHINE COMPRISING (A) A PAIR OF PLATES MOVABLETOWARD AND AWAY FROM EACH OTHER, (B) A FIRST OF SAID PLATES HAVING ACYLINDER AND TWO CHAMBERS THEREIN, (C) SAID CHAMBERS AND CYLINDERINTERSECTING EACH OTHER, (D) A DRIVER PISTON (1) SLIDABLY MOUNTED INSAID CYLINDER AND (2) HAVING (A'') A FIRST END FACE FACING TOWARD ONE OFSAID CHAMBERS AND (B'') AN OPPOSITE SECOND END FACE FACING INTO SAIDCYLINDER, (E) A SEAT MEMBER EXTENDING AROUND AND DEFINING THE OUTERPERIPHERY OF SAID ONE CHAMBER DISPOSED IN POSITION TO ENGAGE SAID PISTONTO CUT OFF DIRECT COMMUNICATION BETWEEN SAID ONE CHAMBER AND BOTH SAIDCYLINER AND THE SECOND OF SAID CHAMBERS,